High speed pump



v D. E. SINGELMANN March 17, 1964 HIGH SPEED PUMP 5 Sheets-Sheet 1 Filed Oct. 1'7, 1962 INVENTOR. DIETRlC H E SINGfLMAI/N i-r TOPNEE {gm March 17, 1964 D. E. SINGELMANN 3,125,029

HIGH SPEED PUMP Filed Oct. 17, 1962 5 Sheets-Sheet 2 INVENTOR D/ETR/CH E. SINGEL/MNN am, @MMwm AT T OPNEYS March 17, 1964 D. E. SINGELMANN 3,125,029

HIGH SPEED PUMP Filed Oct. 17, 1962 5 Sheets-Sheet 3 INVENTOR. fi/E'TE/CH SINGEL/VA/V/V [AT T0 NE March 17, 1964 D. E. SINGELMANN 3,125,029

HIGH SPEED PUMP Filed Oct. 1'7, 1962 5 Sheets-Sheet 4 INVENTOR. DIE TQICH E .SlNGELMAN/Y QMQMJM 6 $3M 'ATTOR EYs March 17, 1964 D. E. SINGELMANIN HIGH SPEED PUMP 5 Sheets-Sheet 5 Filed Oct. 17, 1962 INVENTOR. o/zrmcl/ 5 m; mlwv QEYS United States Patent Office 3,1253% Patented Mar. 17., 1964 3,125,025? HIGH SPEED PUB E Dietrich E. Singelmann, nyder, N.Y., assignor to Bell Aerospace (Iorporation Filed Oct. 17, 1962, Ser. No. 231,174 4 Claims. (Cl. 163-106) This invention relates to fluid pump mechanisms and in particular pertains to certain improvements therein leading to the construction of a highly efiicient pump mechanism characterized by its ability to produce a high output pressure and high mass flow while at the same time being of relatively compact construction.

Although the pump construction according to present invention could be used for any desried purpose, it is a specific objective of the present invention to provide an improved pump structure for supplying hydraulic drive for automotive vehicles and, in particular, the present invention is directed to the pump mechanism of a hydraulic drive for automative vehicles in which the pump is characterized by a high degree of efficiency throughout its operating range so as to avoid the relative inefliciency of normal hydraulic couplings and automatic transmissions associated with automotive vehicles, particularly as regards the low efiiciency which is prevalent at low vehicular speeds. More particularly, the present invention relates to a small, compact fluid pump unit which is capable of operating at relatively high rotational speeds and, for that reason, can readily be driven directly from a high rotational speed prime mover such as a turbine, the pump assembly being characterized by constructional features which not only impart a high degree of efficiency thereto but which also permit of extreme compactness in manufacture so as to exhibit a minimum of weight and as to require a minimum of space for installing the same.

In accord with the present invention, a series of pump assemblies are disposed in stacked relationship with each other within a common housing or body, the body being provided with inlet and outlet manifold assemblies compactly related thereto and wherein the inlet manifold assemblies are connected to the individually stacked pump units by means of selector valve mechanisms which permit the separate pump assemblies to be operated in series or parallel, as desired, in order to vary the torque characteristics of the pump unit and thereby correspondingly coordinate with the operational speed of the vehicle and the operational low characteristics thereof.

A further object of this invention resides in the provision of an improved pump assembly for the purposes hereinabove stated in which a dimensionally small and compact body is provided with specifically oriented and cooperatively related component portions thereof so as to permit the body of the pump assembly to be machined in those regions thereof which would exhibit the greatest loss of efiiciency were such regions not smoothly and properly contoured.

A further object of this invention is to provide an improved pump assembly as aforesaid which incorporates a pair of inlet manifolds and a single outlet manifold with there being valve assemblies associated with each of the inlet manifolds for selectively directing the fluid flow in desired and proper fashion to a plurality of closely spaced and compactly mounted pump assemblies so as to permit the pump assemblies to be operated in series or in parallel or in combinations thereof, as desired, and wherein the discharge path from each of the pump assemblies is so oriented and located with respect to the manifold assemblies as to permit the discharge or diffuser portions to be fully machined during manufacture so as to provide and afford a smooth discharge passage from each of the pump assemblies and to thereby correspondingly reduce power losses.

Other objects and advantages of the invention will appear from the description hereinbelow and the accompanying drawing wherein:

FIG. 1 is a transverse sectional view taken through a pump assembly constructed in accordance with the present invention;

FIG. 2 is a longitudinal section taken through the pump assembly generally along the plane of section line 2-2 in FIG. 1; and

FIGS. 3, 4 and 5 are diagrammatic perspectives indicating the position of the control valves and the flow paths of the fluid in various drive positions of the pump assembly.

Referring now more particularly to FIG. 2, the pump assembly will be seen to include a body '10 provided with a recess 12 which is open at one end 14 of the body so as to receive the stacked pump units indicated generally by the reference character 16 therewithin, there being an end plate 18 removably fixed in a suitable fashion to the body it) to define a closure at that end of the body. The assembly 16 comprises a first stator ring 20, bearing ring 22, a second stator ring 24, a divider and bearing ring 26, a third stator ring 28, a bearing ring 30 and the final stator ring 32, all disposed in stacked relationship as is clearly shown in FIG. 2 and operatively nested within the recess 12 formed in the body 10. A drive shaft 34- projects into the body 10 as shown, a suitable seal assembly 36 being provided just outboard of a suitable ball or roller bearing 38 which is seated within the body 10 and a reduced diameter portion 40 of the shaft 34 projects into the recess 12 and through the various rings aforementioned. Keyed or otherwise suitably fixed to the shaft portion 46 are a series of impellers 42, 44, 46 and as, it being noted that the two impellers 42 and 44 face in the same direction whereas the impellers 46 and 48 face in the opposite direction, hub portions 50' and 52 of the respective impellers 44- and 46 being disposed in abutting relationship within the confines of the dividing and bearing ring 26 and being journalled therewithin as by sleeve bearings 54 and 56, as shown.

To hold the several impellers properly positioned and stacked with any suitable and necessary spacer sleeves on the shaft portion 40, there is provided an inhex nut 69. Each of the impellers is of generally similar construction to all of the others and, as is shown for the impeller 42, the same includes a plurality of blades 62 which are generally radially directed and which project laterally from the web portions 64 and which are integrally joined by the shroud ring 66 so that the web 64 and shroud 66 form, in conjunction with any two adjacent blades 62, radially directed passageways or channels from the inlet eye 63 of each impeller. Each of the stator rings 20, 24, 28 and 32 is formed with an intermediate inner annulus 76 which is contoured on one side to closely conform to the shroud ring 66 of each impeller and which is provided with a faired entrance mouth 72 or lip which directs fluid into the inlet eye 68 of each impeller, the stator ring in each case defining an inlet chamber 74 on one side of the web or annulus 70 and housing the associated impeller within the recess 76 on the opposite side of the annulus 70. Each of the bearing rings 22 and 30 carries a sleeve bearing 78 and these bearing rings together with the intermediate ring 26 provide for bearing support of each impeller closely adjacent to the web portion 64 thereof, substantially as is shown.

Referring now to FIG. 1, it will be seen that the body it) is provided with a pair of valve bores 80 and 82, an upper inlet manifold bore 84 and a lower inlet manifold bore 86 as well as an outlet chamber bore 88. It is a particular feature of the present invention to provide these several bores, as well as the recess 12 aforementioned, in cooperatively related disposition so as to not only provide for a compact design for the entire pump assembly but also to permit the pump to operate at greater efficiency due to the fact that the aforementioned relative disposition of the'several bores is such as to permit ready access for machine at those areas and regions of the body 11) wherein the smooth surface characteristics achieved by machining operations, as opposed to passages formed by casting techniques. Specifically, as can be seen in FIG. 1, each of the pump units formed by a single impeller and its associated stator ring and bearing ring is provided with a generally conical discharge passage or diffuser, such as those indicated by reference characters 91) and 92 in 'FIG. 1. It is to be noted that each of these diffusers such as those indicated by reference characters 91) and 92, are disposed generally in tangential relationship to the associated recess 76 in one of the stator rings 21?, 2d, 28 and 32 and that the center line of each of these diffusers passes through one of the bores 81? or 82 and one of the bores 84 and 86. This relationship is also shown in FIG. 2 although the tangential relationship of the diffusers relative to the recesses 76 in the stator rings is not readily ascertained from FIG. 2. However, FIG. 2 does illustrate clearly that the center line of the diffusers such as that indicated by reference character 91), passes through, and preferably intersects with the center line of the bore 82 and also in similar fashion through the bore 86. Referring both to FIGS. 1 and 2, it will be seen that opposite each of these diffusers, the wall portion 94 of the body 11) which separates the two chambers or bores 82 and 86 is provided with an opening 96 so as to communicate the two such bores at that point and the outer wall 98 of the body 14 (see particularly 2) is provided with a suitable tapped opening receiving a plug 101). The purpose for this construction is to perm t access for machining the surface of the diffuser 96, it being appreciated that the other diifusers are similarly formed. For example, in FIG. 2, the plug 102, when removed, permits access of a tool through the tapped opening receiving such plug and the opening 1114 permits such tool to pass into the confines of the chamber 82 and to form the diffuser 106. At this point, it may be well to know that the diffuser 919 is associated with what will hereinafter be termed the first stage of the pump assembly, the diffuser 92 is associated with the second stage of the pump assembly, the diffuser 106 is associated with the third stage of the pump assembly and the diffuser 108 is associated with the fourth stage of the pump assembly. It will be further noted that the first and third diffusers 911 and 1% are associated with the lower bores 82 and 86 while the second and fourth stage diffusers 92 and 188 are associated with the upper bores 89 and 84. In any case, the access for machining as mentioned hereinbefore relative to the two diffusers 9t) and 1116 prevails in the case of all of the diffusers.

Located within the bores 80 and 82 are a pair of cylindrical valve members, one of which is shown in FIG. 1 and is indicated therein by the reference character 110. Each of these valve members is movable between two positions, the purpose of which and the manner of valve interconnection achieved thereby being more clearly apparent hereinafter. Further, each chamber includes a fixed block or passage forming member therein, one of which is shown in the chamber or bore 82 in FIG. 1 and is designated by reference character 112. This particular member 112 continuously connects the inlet 114 of the first stage pump unit to the interior of the chamber 86, it being noted that the chambers 84 and 86 are both connected to a source of fluid, such as a reservoir, any suitable manner of interconnection being achieved as for example by the conduit 116 shown for the lower chamber 86 in FIG. 1. A similar connection will of course be made for the upper chamber 84.

Referring now to FIG. 3, the four pump stages are shown therein diagrammatically by reference characters 118, 120, 122 and 124. The first stage pump unit 118 includes the inlet 114 previously described which is continuously connected to the chamber or manifold 86 through the fixed member 112, the opening between the two chambers 82 and 86 designated by reference character 1313 in FIG. 1 being indicated, in FIG. 3, by the conduit portion 130. The cylindrical valve member in the lower chamber or bore 82 is diagrammatically illustrated in FIG. 3 by the movable portions 132 and 134, it being appreciated that these two members are actually connected for common movement and are in the form of an elongate cylinder provided with the requisite passages therein, as will hereinafter appear. For the upper of the cylindrical valves 111 it will be seen that only one pair of passageways is provided therein, consequently only one portion of this valve is illustrated in FIG. 3.

On the other hand, the reference character 141B represents a fixed passageway forming member, corresponding to the member 112 in the lower bore 82, such member 1- 50 serving to continuously connect the diffuser 1418 of the fourth stage pump 124 with the outlet chamber 88, such connection being indicated by a conduit 142, although it will be understood that a short passageway or bore in the pump body 11? actually serves for such connection. A similar conduit connection 144 is shown leading from the upper chamber 8'!) to the outlet 88 and to illustrate the actual construction of such passageways as are indicated by reference characters 142 and 144 in FIG. 3, the passageway 144 in FIG. 3 is shown by reference character 146 in FIG. 1. Similar passageways 143 and 1513 are shown between the lower chamber 82 and the outlet 88, the former passageway 148 being indicated by reference character 152 in FIG. 1.

Returning to FIG. 3, it will be noted that in the position of the parts, particularly the cylindrical valves, as shown therein, the lower cylindrical valve has a passage 161) which connects the diffuser 91B of the first stage pump unit 118 with the inlet 162 of the second stage pump unit 121). There is a second passage indicated by reference character 164; which forms no connection in the position shown in FIG. 3 but which serves an alternate connection as will hereinafter appear. t the same time, it will be seen that the upper cylindrical valve 110 as a passageway 166 which connects the diffuser 92 of the second stage pump unit 12th with the inlet 168 of the third stage pump unit 122. Lastly, the lower cylindrical valve member has a passageway 170 which connects the diffuser 1% of the third stage pump unit 122 with the inlet 172 of the fourth stage pump unit 124. Thus, with the position of the valves as shown in FIG. 3, it will be appreciated that the fluid flow is from the inlet conduit 116, into the lower inlet manifold 86, through the opening 131) between the two bores 82 and 86, through the passage forming member 112 and into the inlet 114 of the first stage pump unit 118. Fluid is discharged from the first stage pump unit 118 through the diffuser 90 thereof and then through the lower cylindrical valve member, through the passage thereof to the second stage inlet 162 and so on, the several pump units being disposed in series relationship as hereinbefore stated.

FIG. 4 illustrates another position of the valve assemblies for placing the first and second pump stages in series with each other and in parallel with pump stages three and four, the latter of which are also serially related with respect to each other. For this manner of interconnection, the lower cylindrical valve unit remains in the same position as it was in FIG. 3 and the upper cylindrical valve 112 is moved to its alternate position wherein it will be seen that the previously mentioned passageway 166 now connects the diffuser 92 of the second stage pump unit 120 to the outlet chamber 88 through the aforementioned passage 1 14. At the same time, the other passage of the upper valve 112 now serves to connect the inlet 163 of the third stage unit 122 with the upper inlet manifold 84 through the passageway connection 182, such passageway 182 being indicated in dotted lines in FIG. 1. Thus, it will be apparent that the upper cylindrical valve has accomplished the disposition of two sets of the serially connected pumps in parallel relationship. In FIG. 3, low speed operation of a vehicle, for example, will be accomplished by the connection shown. That is, the output of the pump connection as shown in FIG. 3 would be at one-quarter mass flow and at maximum pressure whereas in FIG. 4, the output of the pump assembly as connected would be one-half total mass flow and one-half total pressure. FIG. 5 illustrates the high speed connection, for vehicular use for example, wherein the four pump stages 113, 120, 122 and 124 are connected in parallel. In the position of the valves shown in FIG. 5, the upper valve 112 is in the same position as it was in FIG. 4 whereas now the lower cylindrical valve is in its alternate position. In this alternate position, the passageway 160 now connects the inlet manifold 86, through the passage 96, to the inlet 162 of the second stage pump and the passageway 164 now connects the diffuser 90 of the first stage pump unit 118, through the passageway 148, to the outlet or discharge manifold 88. Similarly, the passageway 170 now connects the inlet 172 of the fourth stage pump, through the passageway 104, to the inlet manifold 36 and the passageway 200 now connects the diffuser 106 of the third stage pump unit 122, through the passageway 150, to the outlet or discharge manifold 88. Thus, in the position of the parts shown in FIG. 5, the pump output is at full mass rate flow and at one-quarter maximum pressure.

The pump constructed in accordance with the present invention operates at relatively high rotational speeds and achieves unexpectedly high efficiency. For example, the pump may operate at rotational speeds in the order of 55,000 r.p.m. with a maximum outlet pressure of 7100 p.s.i. and a maximum mass rate of flow of 120 gpm. At the same time, the pump unit is extremely compact and lightweight, permitting pump units capable of delivering in the order of 500 H.P. to be made of extremely compact and lightweight design.

It is to be understood that certain changes and modifications as illustrated and described may be made Without departing from the spirit of the invention or the scope of the following claims.

I claim:

1. A compound pump assembly comprising a body having a bore therein,

a plurality of centrifugal pump devices received in said bore, each such pump device having an annular discharge chamber and an inlet,

shaft means for driving said pump devices,

said body also having a valve bore and an inlet bore, with the valve and inlet bores being substantially parallel to each other and to the first mentioned bore and with the axes of the valve and inlet bores aligned on a straight line tangentially intersecting the discharge chambers of said pump devices,

valve means received in said valve bore,

said body having a discharge passage from each of said outlet chambers extending tangentially therefrom to said valve bore along a line passing through the axes of said valve and inlet bores, and an inlet passage from said valve bore to the inlet of each pump device, said body also having discharge passages extending from said valve bore externally of said body,

said valve means having ports for alignment with said inlet passages and said outlet passages for selectively connecting said pump devices in series and in parallel.

2. A compound pump assembly comprising a body having a housing portion,

a plurality of pump devices received in said housing portion, each including a stator and an impeller, each stator having an intermediate annulus providing an inlet chamber on one side of said annulus and an outlet chamber on the other side of said annulus with the two such chambers being connected by the opening presented by said annulus, each impeller being located within its associated outlet chamber to receive fluid from the inlet chamber through the opening in said annulus and discharge such fluid within the associated discharge chamber,

said body also having a valve bore and an inlet bore,

with the valve and inlet bores being substantially parallel to each other and to the first mentioned bore and with the axes of the valve and inlet bores aligned on a straight line tangentially intersecting the discharge chambers of said pump devices,

valve means received in said valve bore,

said body having a discharge passage from each of said outlet chambers extending tangentially therefrom to said valve bore along a line passing through the axes of said valve and inlet bores, and an inlet passage from said valve bore to the inlet of each pump device, said body also having discharge passages extending from said valve bore externally of said body,

said valve means having ports for alignment with said inlet passages and said outlet passages for selectively connecting said pump devices in series and in parallel.

3. In a centrifugal pump assembly adapted for direct drive connection to a source of high speed rotational power, comprising an elongate body having a plurality of longitudinally extending bores presenting a pump-receiving bore, upper and lower valve bores and upper and lower inlet bores,

a plurality of centrifugal pumps received in said bore,

each having an annular outlet chamber,

said upper valve bore and said upper inlet bore being disposed relative to each other and to said pumpreceiving bore so that a straight line passed through the axes of the former intersects the pump-receiving bore offset from its axis and tangential to said outlet chambers and the lower valve bore and the lower inlet bore being similarly disposed relative to each other and the pump-receiving bore.

4. In a centrifugal pump assembly adapted for direct drive connection to a source of high speed rotational power, comprising an enlongate body having a plurality of longitudinally extending bores presenting a pump-receiving bore, upper and lower valve bores and upper and lower inlet bores,

a plurality of centrifugal pumps received in said bore,

each having an annular outlet chamber,

said upper valve bore and said upper inlet bore being disposed relative to each other and to said pump-receiving bore so that a straight line passed through the axes of the former intersects the pump-receiving bore offset from the axis and tangential to said outlet chambers and the lower valve bore and the lower inlet bore being similarly disposed relative to each other and the pump-receiving bore,

and there being an outlet manifold bore nested between the upper and lower valve and inlet bores.

References Cited in the file of this patent UNITED STATES PATENTS 1,231,310 Taylor June 26, 1917 FOREIGN PATENTS 460,986 Germany June 9, 1928 

1. A COMPOUND PUMP ASSEMBLY COMPRISING A BODY HAVING A BORE THEREIN, A PLURALITY OF CENTRIFUGAL PUMP DEVICES RECEIVED IN SAID BORE, EACH SUCH PUMP DEVICE HAVING AN ANNULAR DISCHARGE CHAMBER AND AN INLET, SHAFT MEANS FOR DRIVING SAID PUMP DEVICES, SAID BODY ALSO HAVING A VALVE BORE AND AN INLET BORE, WITH THE VALVE AND INLET BORES BEING SUBSTANTIALLY PARALLEL TO EACH OTHER AND TO THE FIRST MENTIONED BORE AND WITH THE AXES OF THE VALVE AND INLET BORES ALIGNED ON A STRAIGHT LINE TANGENTIALLY INTERSECTING THE DISCHARGE CHAMBERS OF SAID PUMP DEVICES, VALVE MEANS RECEIVED IN SAID VALVE BORE, SAID BODY HAVING A DISCHARGE PASSAGE FROM EACH OF SAID OUTLET CHAMBERS EXTENDING TANGENTIALLY THEREFROM TO SAID VALVE BORE ALONG A LINE PASSING THROUGH THE AXES OF SAID VALVE AND INLET BORES, AND AN INLET PASSAGE FROM SAID VALVE BORE TO THE INLET OF EACH PUMP DEVICE, SAID BODY ALSO HAVING DISCHARGE PASSAGES EXTENDING FROM SAID VALVE BORE EXTERNALLY OF SAID BODY, SAID VALVE MEANS HAVING PORTS FOR ALIGNMENT WITH SAID INLET PASSAGES AND SAID OUTLET PASSAGES FOR SELECTIVELY CONNECTING SAID PUMP DEVICES IN SERIES AND IN PARALLEL. 